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CN113833701A - Hydraulic system of rotary machine - Google Patents

Hydraulic system of rotary machine Download PDF

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Publication number
CN113833701A
CN113833701A CN202111041495.9A CN202111041495A CN113833701A CN 113833701 A CN113833701 A CN 113833701A CN 202111041495 A CN202111041495 A CN 202111041495A CN 113833701 A CN113833701 A CN 113833701A
Authority
CN
China
Prior art keywords
port
valve
oil
compensation
control valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202111041495.9A
Other languages
Chinese (zh)
Inventor
金月峰
张箭
董玉忠
张洋
孙本强
苗衡
卢杰
张新奎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Xuzhou XCMG Excavator Machinery Co Ltd
Original Assignee
Xuzhou XCMG Excavator Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Xuzhou XCMG Excavator Machinery Co Ltd filed Critical Xuzhou XCMG Excavator Machinery Co Ltd
Priority to CN202111041495.9A priority Critical patent/CN113833701A/en
Publication of CN113833701A publication Critical patent/CN113833701A/en
Priority to PCT/CN2022/107922 priority patent/WO2023035794A1/en
Priority to EP22866268.0A priority patent/EP4368840A1/en
Priority to AU2022343587A priority patent/AU2022343587A1/en
Priority to US18/688,359 priority patent/US12247589B2/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention discloses a hydraulic system of a rotary machine tool, which comprises an oil tank, a main pump, a control valve and a rotary motor, wherein the oil tank is connected with an oil suction port of the main pump, an oil outlet of the main pump is connected with a port P of the control valve, a port T of the control valve is communicated with the oil tank, and a port A of the control valve and a port B of the control valve are connected with two ends of the rotary motor. The control valve comprises a compensation valve, an electric proportional valve and an electromagnetic reversing valve, a P port is connected with a first oil port of the electric proportional valve, the P port is connected with a third oil port of the compensation valve, the P port is connected with a fifth oil port of the compensation valve, a second oil port of the electric proportional valve is connected with a first oil port of the compensation valve, a second oil outlet of the compensation valve is connected with a third oil port of the electromagnetic reversing valve, a second oil outlet of the compensation valve is connected with a T port, a fourth oil outlet of the compensation valve is connected with the T port, a fourth oil port of the electromagnetic reversing valve is connected with the T port, and a second oil port of the electromagnetic reversing valve is connected with a B port. The device of the invention is additionally provided with the control valve, can adjust the flow entering the machine tool motor, and realizes the independent control of the speed of the machine tool motor.

Description

Hydraulic system of rotary machine
Technical Field
The invention relates to a hydraulic system of a rotary machine tool, and belongs to the technical field of flow control of hydraulic systems of excavators.
Background
With the continuous innovation of the excavator accessories, more and more accessories can be installed on the excavator to carry out diversified operation, so that the multifunctional excavator can realize multiple functions, manual operation is replaced, and the operation efficiency is improved. However, in the conventional attachments, oil is supplied by a pump on an original system of the excavator, and when the attachments and the excavator boom and bucket and the like perform combined operation, the operation speed of the attachments and the excavator boom and bucket and the like is reduced, so that the operation efficiency is reduced.
As shown in fig. 2, the rotation motor 4 in the prior art controls the operation direction by the implement control valve 3-4, the boom cylinder 5 controls the cylinder to extend and retract by the boom control valve 3-2, the main pump 2 is connected to both the implement control valve 3-4 and the boom control valve 3-2, and the main pump 2 outputs hydraulic oil to both the implement motor 4 and the boom cylinder 5. The swing motor 4 and the boom cylinder 5 share the same main pump 2, and adjusting the stroke of the boom cylinder 5 during the swing of the swing motor 4 causes the swing speed of the swing motor 4 to decrease rapidly, which affects the working efficiency.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a hydraulic system of a rotary machine tool, wherein the speed of the rotary motor machine tool is not influenced by other actions such as a movable arm, a bucket rod and the like and is independently controlled.
In order to achieve the purpose, the invention provides a hydraulic system of a rotary machine tool, which comprises an oil tank, a main pump, a control valve and a rotary motor, wherein the oil tank is connected with an oil suction port of the main pump, an oil outlet of the main pump is connected with a port P of the control valve, a port T of the control valve is communicated with the oil tank, and a port A of the control valve and a port B of the control valve are connected with two ends of the rotary motor.
Preferably, the control valve comprises a compensation valve, an electro-proportional valve and an electromagnetic reversing valve, the port P is connected with the port I of the electro-proportional valve, the port P is connected with the port III of the compensation valve, the port P is connected with the port V of the compensation valve, the port II of the electro-proportional valve is connected with the port I of the compensation valve, the port II of the compensation valve is connected with the port III of the electromagnetic reversing valve, the port II of the compensation valve is connected with the port T, the port IV of the electromagnetic reversing valve is connected with the port T, and the port II of the electromagnetic reversing valve is connected with the port B.
Preferably, the control valve comprises an overflow valve, the port P is connected with the first overflow valve port, and the second overflow valve port is connected with the port T.
Preferably, the control valve comprises a first port overflow valve, the fourth electromagnetic directional valve oil port is connected with the first port overflow valve oil port, the second first port overflow valve oil port is connected with the port A, and the second first port overflow valve oil port is connected with the first electromagnetic directional valve oil port.
Preferably, the control valve comprises a second port overflow valve, the second electromagnetic directional valve oil port is connected with the first second port overflow valve oil port, the second port overflow valve oil port is connected with the T port, and the first second port overflow valve oil port is communicated with the B port.
Preferably, the electromagnetic directional valve is a three-position four-way electromagnetic directional valve, the left position of the three-position four-way electromagnetic directional valve is that the first oil port is communicated with the third oil port and the second oil port is communicated with the fourth oil port, and the right position of the three-position four-way electromagnetic directional valve is that the first oil port is communicated with the fourth oil port and the second oil port is communicated with the third oil port.
Preferably, the compensation valve comprises a throttle valve, and the compensation valve oil outlet two-way is connected with the T port through the throttle valve.
The invention achieves the following beneficial effects:
the rotary motor is independently controlled, the forward and reverse rotation control of the rotary motor is realized by switching the left position and the right position of the electromagnetic reversing valve, the oil circuit of the rotary motor is switched on and off by the electro-proportional valve and the compensating valve, other actions such as a movable arm, a bucket rod and the like are realized in the rotating process of the rotary motor, the rotating speed of the rotary motor is not influenced, and the working efficiency of the whole machine is improved;
when the rotary motor rotates clockwise, if the electromagnetic directional valve is powered off, the middle position of the electromagnetic directional valve works, the main pump is disconnected with the oil circuit of the rotary motor, the oil circuit of the hydraulic oil tank is disconnected with the oil circuit of the rotary motor, the rotary motor continues to rotate clockwise under the action of inertia, the pressure in the pipelines from A to C is reduced, the pressure in the pipelines from D to B is increased, the first port overflow valve sucks oil from the hydraulic oil tank and supplements the oil to the pipelines from A to C to prevent the oil from being sucked, and the second port overflow valve discharges high-pressure oil from D to B into the hydraulic oil tank to prevent the system from being overloaded.
When the rotary motor rotates anticlockwise, if the electromagnetic reversing valve is powered off, the middle position of the electromagnetic reversing valve works, the oil circuit of the main pump and the rotary motor is disconnected, the hydraulic oil tank and the oil circuit of the rotary motor are disconnected, the rotary motor continues to rotate anticlockwise under the action of inertia, the pressure in the pipelines from A to C rises, the pressure in the pipelines from D to B decreases, at the moment, high-pressure oil in the pipelines from A to C in the first port overflow valve is discharged to the hydraulic oil tank, the system overload is prevented, the second port overflow valve absorbs oil from the hydraulic oil tank and supplements the oil to the pipelines from D to B to prevent the oil from being sucked, all hydraulic oil in the oil circuit is prevented from flowing into the oil tank, and the smoothness of the whole oil circuit in working is guaranteed.
Drawings
FIG. 1 is an oil circuit diagram of the present invention;
fig. 2 is an oil path diagram of a swing motor and a boom cylinder in the related art.
Reference sign, 1, oil tank; 2. a main pump; 3. a control valve; 4. a rotary motor; 31. a compensation valve; 32. an electro proportional valve; 33. a first port relief valve; 34. a second port relief valve; 35. an electromagnetic directional valve; 36. a throttle valve; 37. an overflow valve; 3-1, a first one-way valve; 3-2, moving arm reversing valves; 3-3, a second one-way valve; 3-4, rotating a motor reversing valve; 3-5, a first oil replenishing valve; 3-6, a first overflow valve; 3-7, a second one-way valve; 3-8 and a second overflow valve.
Detailed Description
The following examples are only for illustrating the technical solutions of the present invention more clearly, and the protection scope of the present invention is not limited thereby.
It should be noted that, if there is a directional indication (such as up, down, left, right, front, and back) in the embodiment of the present invention, it is only used to explain the relative position relationship between the components, the motion situation, and the like in a certain posture, and if the certain posture is changed, the directional indication is changed accordingly.
In addition, if the description of "first", "second", etc. is referred to in the present invention, it is used for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
The novel hydraulic system and the control valve of the rotary machine tool of the excavator mainly comprise a hydraulic oil tank 1, a main pump 2, a control valve 3, a rotary motor 4 and a movable arm oil cylinder 5, wherein the control valve 3 comprises a 31 compensating valve, a 32 electric proportional valve, a 33 first-port overflow valve, a 34 second-port overflow valve, a 35 electromagnetic directional valve, a 36 throttle valve and a 37 overflow valve.
An oil suction port F of a main pump 2 is connected with an oil tank 1, an oil outlet E of the main pump 2 is connected with a port P of a control valve 3, the port P is connected with a first overflow valve port 37, a second overflow valve port 37 is connected with a port T, the port T is connected with the hydraulic oil tank 1, the port P is connected with a first electric proportional valve 32, the port P of the control valve 3 is connected with a third compensation valve 31, the port P is connected with a fifth compensation valve 31, a second electric proportional valve 32 is connected with the first compensation valve 31, a second compensation valve 31 oil outlet is connected with a throttle valve 36, a second compensation valve 31 oil outlet is connected with a third electromagnetic reversing valve 35, an oil outlet of the throttle valve 36 is connected with the port T, an oil outlet 4 of the compensation valve 31 is connected with the port T, a fourth electromagnetic reversing valve 35 oil outlet is connected with a first overflow valve 33, the second oil port of the first port overflow valve 33 is connected with the port A, the second oil port of the first port overflow valve 33 is connected with the first oil port of the electromagnetic directional valve 35, the second oil port of the electromagnetic directional valve 35 is connected with the port B, the second oil port of the electromagnetic directional valve 35 is connected with the first oil port of the second port overflow valve 34, the second oil port of the second port overflow valve 34 is connected with the port T, the first oil port of the second port overflow valve 34 is communicated with the port B, the port A is connected with the port C of the rotary motor 4, and the port B is connected with the port D of the rotary motor 4.
The working principle of the invention formed in this way is as follows:
after the excavator is started, the engine drives the main pump 2 to work, the main pump 2 outputs hydraulic oil to enter a port P of the control valve 3, when the rotary motor 4 does not need to work, an internal oil circuit is disconnected under the condition that the electric proportional valve 32 is not electrified, and the hydraulic oil output by the main pump 2 is communicated into the hydraulic oil tank 1 through the compensating valve 31;
when the rotary motor 4 needs to work, the left electromagnet or the right electromagnet of the electromagnetic reversing valve 35 and the electro-proportional valve 32 are electrified, the current of the electro-proportional valve 32 can be adjusted and controlled according to the speed requirement, the opening area of an oil path in the electro-proportional valve 32 is realized, hydraulic oil is output by the main pump 2, passes through the oil path in the electro-proportional valve 32, passes through an oil path in the compensation valve 31, passes through the oil path in the electromagnetic reversing valve 35, enters the rotary motor 4, and drives the rotary motor 4 to rotate;
when the electromagnet on the left side of the electromagnetic directional valve 35 is electrified, the electromagnetic directional valve 35 works on the left side, hydraulic oil output by the main pump 2 passes through the left side of the electromagnetic directional valve 35 and enters the rotary motor 4 through the port A and the port C, and the rotary motor 4 rotates clockwise; when the electromagnet on the right side of the electromagnetic directional valve 35 is electrified, the electromagnetic directional valve 35 works in the right position, hydraulic oil output by the main pump 2 passes through the right position of the electromagnetic directional valve 35 and enters the rotary motor 4 through a port D of a port B, and the rotary motor 4 rotates anticlockwise;
when the load of the rotary motor 4 is too large and can not rotate, the hydraulic oil output by the main pump 2 is discharged to the hydraulic oil tank 1 through the overflow valve 37, when the rotary motor 4 rotates clockwise, if the electromagnetic directional valve 35 is powered off, the middle position of the electromagnetic directional valve 35 works, the oil passages of the main pump 2 and the rotary motor 4 are disconnected, the oil passages of the hydraulic oil tank 1 and the rotary motor 4 are disconnected, the rotary motor 4 continues to rotate clockwise under the action of inertia, the pressure in the pipelines from A to C is reduced, the pressure in the pipelines from D to B is increased, at the moment, the oil in the first port overflow valve 33 is absorbed from the hydraulic oil tank 1 and supplemented to the pipelines from A to C, the air absorption of the pipeline is prevented, and the high-pressure oil in the pipelines from D to B is discharged to the hydraulic oil tank 1 through the second port overflow valve 34, so that the system is prevented from being overloaded.
When the rotary motor 4 rotates anticlockwise, if the electromagnetic directional valve 35 is powered off, the middle position of the electromagnetic directional valve 35 works, the oil way of the main pump 2 and the oil way of the rotary motor 4 is disconnected, the oil way of the hydraulic oil tank 1 and the oil way of the rotary motor 4 are disconnected, the rotary motor 4 continues to rotate anticlockwise under the action of inertia, the pressure in the pipeline from A to C is increased, the pressure in the pipeline from D to B is reduced, at the moment, high-pressure oil in the pipeline from A to C in the first port overflow valve 33 is discharged to the hydraulic oil tank 1 to prevent the system from being overloaded, and the second port overflow valve 34 absorbs oil from the hydraulic oil tank 1 and supplements the oil to the pipeline from D to B to prevent the oil from being sucked.
The device of the invention is additionally provided with the control valve, can adjust the flow entering the machine tool motor, and realizes the independent control of the speed of the machine tool motor. The speed of the rotary motor tool is not influenced by other actions such as a movable arm, a bucket rod and the like, and the rotary speed can be adjusted in real time according to the working condition requirement; the invention has simple and reliable structure and good universality and is suitable for industrialized popularization and application.
The hydraulic oil tank 1, the main pump 2, the rotary motor 4, the boom cylinder 5, the compensating valve 31, the 32 electro-proportional valve, the first port overflow valve 33, the second port overflow valve 34, the electromagnetic directional valve 35, the throttle valve 36 and the overflow valve 37 are various in types that can be adopted in the prior art, and those skilled in the art can select a suitable type according to actual requirements, and the embodiment is not illustrated.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (7)

1. The utility model provides a rotary machine hydraulic system, which is characterized in that, includes oil tank (1), main pump (2), control valve (3) and rotating motor (4), and the oil-suction opening of main pump (2) is connected in oil tank (1), and the P mouth of oil-out connection control valve (3) of main pump (2), the T mouth intercommunication oil tank (1) of control valve (3), and the A mouth of control valve (3) and the B mouth of control valve (3) are connected rotating motor (4) both ends.
2. A rotary implement hydraulic system according to claim 1,
the control valve (3) comprises a compensation valve (31), an electro-proportional valve (32) and an electromagnetic reversing valve (35), a port P is connected with a port I of the electro-proportional valve (32), the port P is connected with a port III of the compensation valve (31), the port P is connected with a port V of the compensation valve (31), a port II of the electro-proportional valve (32) is connected with a port I of the compensation valve (31), a port II of the compensation valve (31) is connected with a port III of the electromagnetic reversing valve (35), a port T is connected with a port II of the compensation valve (31), a port IV of the compensation valve (31) is connected with the port T, a port IV of the electromagnetic reversing valve (35) is connected with the port T, and a port II of the electromagnetic reversing valve (35) is connected with a port B.
3. A rotary implement hydraulic system according to claim 1, characterized in that the control valve (3) comprises an overflow valve (37), the first port of the overflow valve (37) is connected to the P port, and the second port of the overflow valve (37) is connected to the T port.
4. A rotary implement hydraulic system according to claim 2, wherein the control valve (3) comprises a first port overflow valve (33), the fourth port of the electromagnetic directional valve (35) is connected to the first port overflow valve (33), the second port of the first port overflow valve (33) is connected to the port a, and the second port overflow valve (33) is connected to the first port of the electromagnetic directional valve (35).
5. A rotary implement hydraulic system according to claim 2, wherein the control valve (3) comprises a second port overflow valve (34), the second port of the electromagnetic directional valve (35) is connected with the first port of the second port overflow valve (34), the second port overflow valve (34) is connected with the T port, and the first port of the second port overflow valve (34) is communicated with the B port.
6. The rotary machine hydraulic system of claim 2, wherein the electromagnetic directional valve (35) is a three-position four-way electromagnetic directional valve, the left position of the three-position four-way electromagnetic directional valve is provided with a first oil port and a third oil port and a second oil port and a fourth oil port, and the right position of the three-position four-way electromagnetic directional valve is provided with a first oil port and a fourth oil port and a second oil port and a third oil port.
7. A rotary implement hydraulic system according to claim 2,
comprises a throttle valve (36), and an oil outlet two-way of the compensation valve (31) is connected with a T port through the throttle valve (36).
CN202111041495.9A 2021-09-07 2021-09-07 Hydraulic system of rotary machine Pending CN113833701A (en)

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CN202111041495.9A CN113833701A (en) 2021-09-07 2021-09-07 Hydraulic system of rotary machine
PCT/CN2022/107922 WO2023035794A1 (en) 2021-09-07 2022-07-26 Hydraulic system for rotary machine tool
EP22866268.0A EP4368840A1 (en) 2021-09-07 2022-07-26 Hydraulic system for rotary machine tool
AU2022343587A AU2022343587A1 (en) 2021-09-07 2022-07-26 Hydraulic system for rotary machine tool
US18/688,359 US12247589B2 (en) 2021-09-07 2022-07-26 Hydraulic system for rotary implement

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Application publication date: 20211224